US4728086A - Vibration isolating apparatus - Google Patents
Vibration isolating apparatus Download PDFInfo
- Publication number
- US4728086A US4728086A US07/000,126 US12687A US4728086A US 4728086 A US4728086 A US 4728086A US 12687 A US12687 A US 12687A US 4728086 A US4728086 A US 4728086A
- Authority
- US
- United States
- Prior art keywords
- partition
- liquid chambers
- vibration isolating
- tube
- isolating apparatus
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/20—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper characterised by comprising also a pneumatic spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
- F16F13/1427—Units of the bushing type, i.e. loaded predominantly radially characterised by features of flexible walls of equilibration chambers; decoupling or self-tuning means
Definitions
- the present invention relates to a vibration isolating apparatus which has an inner tube and an outer tube and which may be employed as an engine mount of the like.
- Vibration isolating apparatuses include a so-called bush type rubber vibration isolator in which an inner tube and an outer tube are disposed coaxially or axially parallel with each other, and one type of such vibration isolating apparatus wherein a liquid chamber is provided in a resilient member disposed between the inner and outer tubes has already been proposed (see Japanese Patent Laid-Open No. 179542/1985).
- the liquid chamber is partitioned into a plurality of small liquid chambers, and these chambers are communicated with each other through an orifice. If the dimensions of this orifice are set so as to damp low-frequency vibrations of relatively large amplitude, when a high-frequency vibration of relatively small amplitude occurs, the dynamic scale factor is increased and this causes the vibration transmitting characteristics to be undesirably deteriorated. Conversely, if the dimensions of the orifice are set so as to improve the vibration transmitting characteristics for high-frequency vibrations of relatively small amplitudes, it is impossible to damp low-frequency vibrations of relatively large amplitude, disadvantageously.
- the present invention provides a vibration isolating apparatus comprising: an inner tube which is able to be connected to either one of a vibration generating portion and a vibration receiving portion; an outer tube disposed on the outer peripheral portion of the inner tube so that the inner and outer tubes are coaxial or axially parallel with each other, the outer tube being able to be connected to the other of the vibration generating portion and the vibration receiving portion; a vibration absorbing resilient member interposed between the inner and outer tubes; a pair of liquid chambers provided in the resilient member so as to oppose each other across the inner tube; a limiting passage for providing communication between the pair of liquid chambers; a flexible membrane for partitioning each of the liquid chambers and an air chamber from each other, the air chamber being provided adjacent to the liquid chamber; and a partition for partitioning each of the liquid chambers into a plurality of small liquid chambers, the partition having a flow passage for providing communication between the small liquid chambers
- the apparatus according to the present invention enables absorption of vibrations over a widened frequency range.
- the volumetric capacity of the air chamber is preferably made substantially equal to the amount of fluid which is moved by a high-frequency vibration of relatively small amplitude, and the cross-sectional area of the flow passage defined by the partition is preferably set so as to be larger than that of the limiting passage.
- FIG. 1 shows a first embodiment of the vibration isolating apparatus according to the present invention, which corresponds to a sectional view taken along the line I--I in FIG. 2;
- FIG. 2 is a sectional view taken along the line II--II in FIG. 1;
- FIG. 3 is a sectional view of a second embodiment of the present invention, which corresponds to FIG. 1;
- FIG. 4 is a fragmentary enlarged view of a part of the vibration isolating apparatus shown in FIG. 3;
- FIG. 5 is a sectional view taken along the line V--V in FIG. 3;
- FIG. 6 is a sectional view of a third embodiment of the present invention, which corresponds to FIG. 1;
- FIG. 7 is a sectional view taken along the line VII--VII in FIG. 6;
- FIG. 8 is a sectional view of a fourth embodiment of the present invention, which corresponds to FIG. 1;
- FIG. 9 is a sectional view taken along the line IX--IX in FIG. 8;
- FIG. 10 is a sectional view of a fifth embodiment of the present invention, which corresponds to FIG. 1;
- FIG. 11 is a sectional view taken along the line XI--XI in FIG. 10.
- FIGS. 1 and 2 show in combination a first embodiment of the vibration isolating apparatus according to the present invention.
- the vibration isolating apparatus 10 has an inner tube 12 and an outer tube 14 which are disposed coaxially with each other.
- the inner tube 12 is connected to a vibration generating portion (not shown) such as a wheel of an automobile, and the outer tube 14 is connected to a vibration receiving portion (not shown) such as the body of the vehicle.
- An intermediate tube 16 is coaxially disposed inside the outer tube 14. Two axial end portions of the tube 16 are bent outward, and two axial end portions of the outer tube 14 are bent inward to define bent portions 14A so that the bent portions 14A are pressed against the bent end portions of the intermediate tube 16, respectively, and the tube 16 is thereby rigidly secured to the outer tube 14.
- a tubular rubber member 18 is bonded to the inner peripheral portion of the intermediate tube 16 and the outer peripheral portion of the inner tube 12 by means of vulcanization.
- the outer tube 14 is secured to the rubber member 18 through the intermediate tube 16.
- the rubber member 18 is provided with a pair of hollow portions which extend from the outer periphery of a substantially axially central portion of the inner tube 12 in opposite directions symmetrically with each other with respect to the axial center of the inner tube 12 and which are filled with a fluid such as water or oil in such a manner that the fluid is tightly sealed therein, thus defining two liquid chambers 20 and 22.
- a ring 24 is rigidly secured to the outer periphery of a portion of the inner tube 12 which faces the liquid chambers 20 and 22.
- the ring 24 is provided in the inner peripheral portion thereof with a groove 26 which surrounds the outer periphery of the inner tube 12 and which is communicated with the liquid chambers 20 and 22 through small bores 28 and 30, respectively.
- the groove 26 serves as a limiting passage which provides communication between the liquid chambers 20 and 22.
- the intermediate tube 16 is cut at portions which respectively face the liquid chambers 20 and 22 so as to provide cut portions 32, thereby extending the liquid chambers 20 and 22 to the outside of the intermediate tube 16.
- flexible membranes 34 are provided so as to face the liquid chambers 20 and 22, respectively, in such a manner that the peripheral portion of each membrane 34 is clamped between the intermediate tube 16 and the outer tube 14.
- One surface of each membrane 34 faces the liquid chamber 20 (or 22), and the other surface thereof cooperates with the outer tube 14 to define an air chamber 36 therebetween.
- the volumetric capacity of the air chamber 36 is preferably made substantially equal to the amount of liquid moving between the liquid chambers 20 and 22 when a high-frequency vibration of relatively small ampliture occurs.
- Partitions 38 are provided on the inner peripheral side of the intermediate tube 16 so that they partition the liquid chambers 20 and 22, respectively.
- each of the liquid chambers 20 and 22 is partitioned into two small liquid chambers.
- Two longitudinal end portions of each partition 38 are supported by opposing walls of the liquid chamber 20 (or 22) as shown in FIG. 2, but two lateral end portions thereof define flow passages 40 between the same and the other opposing walls of the liquid chamber 20 (or 22) as shown in FIG. 1.
- the cross-sectional area of each flow passage 40 is made larger than that of the groove 26 and set so that liquid-column resonance readily occurs when high-frequency vibrations act on the apparatus.
- a seal rubber member 42 is enclosed in the area between the inner tube 12 and the intermediate tube 16.
- the inner tube 12 is rigidly secured to a vibration source such as an automotive wheel (not shown), and the outer tube 14 to the body of the vehicle or the like.
- Vibrations mainly act on the inner tube 12 in a direction perpendicular to the axis thereof.
- a low-frequency vibration of relatively large amplitude acts on the inner tube 12
- the vibration is absorbed by means of the fluid resistance which occurs when the liquid moves between the liquid chambers 20 and 22 through the groove 26.
- the groove 26 When a high-frequency vibration of relatively small amplitude occurs, the groove 26 may be clogged or loaded. In such case, in response to the rise and fall in internal pressure in the liquid chambers 20 and 22, the air chambers 36 are expanded and contracted. In consequence, the liquid within each of the liquid chambers 20 and 22 moves through the flow passages 40, causing liquid-column resonance to occur at the flow passages 40, and resulting in a lowering of the dynamic scale factor, advantageously.
- FIGS. 3 to 5 there is shown a second embodiment of the present invention.
- each partition 38 is received in an annular recess 44 which is formed in the rubber member 18, and a small bore 46 is provided in the center of each partition 38 to define a flow passage.
- the overall length b of the partition 38 is greater than the distance a between the opposing walls of each of the liquid chambers 20 and 22 but smaller than the distance c between the opposing bottom portions of the annular recess 44. It is preferable to set the relationship between a, b and c as follows:
- the partition 38 can readily be fitted into the recess 44, and the rubber member 18 is allowed to move smoothly when vibrations of relatively large amplitude act thereon.
- the distance h between the outer surface of the partition 38 and the inner surface of the intermediate tube 16 is preferably minimized in order to facilitate fitting of the partition 38 into the recess 44.
- positioning the partition 38 closer to the air chamber 36 causes an increase in the amount of vibratory deformation (surface area) of a portion of the rubber member 18 which defines a small liquid chamber on the side of the partition 38 which is remote from the air chamber 36, so that the amount of liquid which is moved by vibrations increases to allow liquid-column resonance to occur even more easily at the small bore 46, thus enabling a great lowering of the dynamic scale factor at the time of occurrence of high-frequency vibrations of relatively small amplitude.
- each air chamber 36 is communicated with the outside air through an opening 47 provided in the outer tube 14, thereby facilitating the assembly. More specifically, any fluid which undesirably enters the air chamber 36 through opening 47 during assembly can readily be removed through the opening 47. Further, when the outer tube 14 is press-fitted into a hollow portion of a vehicle body or the like, the openings 47 serve to prevent any excessive rise in pressure in the air chamber 36 and thereby to allow liquid-column resonance to readily occurr in the liquid chambers 20 and 22.
- FIGS. 6 and 7 show in combination a third embodiment of the present invention.
- each partition 48 is clamped at its peripheral portion between the intermediate tube 16 and the flexible membrane 34.
- the partition 48 has its intermediate portion projecting into the liquid chamber 20 (or 22) to a substantial extent, and small bores 46 are provided in the side walls, respectively, of this projecting portion.
- this embodiment has no fear of the rubber member 18 being damaged, since the partitions 48 in this embodiment are moved relative to the rubber member 18 in response to the elastic deformation of the latter. Further, since the rubber member 18 has no grooves for receiving the partitions 48, there is no concentration of stress which would otherwise occur around each groove.
- each partition 48 projects into the corresponding liquid chamber 20 (or 22) and is able to come into contact with the ring 24, it can also serve as a stopper.
- a thin-walled portion 18A which is integral with the rubber member 18 and extended therefrom is provided on the outer periphery of the ring 24 for cushioning the impact of the intermediate portion of the partition 48.
- the static characteristics of the vibration isolating apparatus can be made linear, and therefore employment of the apparatus for a suspension of an automobile enables a great improvement in steering stability.
- the arrangement in accordance with this embodiment improves the durability of the rubber member 18.
- FIGS. 8 and 9 there is provided a fourth embodiment of the present invention.
- two opposing axially central portions of the intermediate tube 16 are drawn toward the inner tube 12 to define grooves 52, two axial ends of each groove 52 being communicated with the liquid chambers 20 and 22, respectively.
- this embodiment needs no ring such as the ring 24 which is fitted on the outer periphery of the inner tube 12 in the first embodiment, and each groove 52 serves as a limiting passage which provides communciation between the liquid chambers 20 and 22.
- the area between the intermediate tube 16 and the outer tube 14 except for the groove 52 is hermetically sealed with the seal rubber member 42.
- FIGS. 10 and 11 show in combination a fifth embodiment of the present invention.
- the intermediate tube 16 in accordance with the first embodiment is cut at the axially central portion into intermediate tube members 16A and 16B, which are individually bonded to the outer periphery of the rubber member 18 by means of vulcanization.
- Groove members 54 are disposed between the intermediate tube members 16A and 16B, each member 54 having a U-shaped cross-section as shown in FIG. 10 and a C-shaped configuration in side view as shown in FIG. 11.
- each U-shaped groove member 54 is closed by the inner peripheral surface of the outer tube 14, while the outer peripheries of the other side portions of the groove member 54 are bonded to the rubber member 18 by means of vulcanization, and two axial ends of the groove member 54 are communicated with the liquid chambers 20 and 22, respectively.
- each of the groove members 54 serves as a limiting passage for providing communication between the liquid chambers 20 and 22.
- this embodiment enables the apparatus to be readily produced at low costs as compared with the above-described embodiments, and permits the cross-sectional area of the limiting passage to be ensured at a appropriate value.
- the outer tube 14 and the inner tube 12 may be secured to a vibration generating portion and a vibration receiving portion, respectively, in a reverse manner to that in the above-described embodiments.
Abstract
Description
(c-b)<(c-a) /2
Claims (20)
(c-b)<(c-a)/2
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP61-9705 | 1986-01-20 | ||
JP61009705A JPH0689806B2 (en) | 1986-01-20 | 1986-01-20 | Anti-vibration device |
Publications (1)
Publication Number | Publication Date |
---|---|
US4728086A true US4728086A (en) | 1988-03-01 |
Family
ID=11727654
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US07/000,126 Expired - Lifetime US4728086A (en) | 1986-01-20 | 1987-01-02 | Vibration isolating apparatus |
Country Status (2)
Country | Link |
---|---|
US (1) | US4728086A (en) |
JP (1) | JPH0689806B2 (en) |
Cited By (47)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4817926A (en) * | 1987-04-04 | 1989-04-04 | Firma Carl Freudenberg | Hydraulically damped tubular rubber spring |
FR2622661A1 (en) * | 1987-10-28 | 1989-05-05 | Bridgestone Corp | VIBRATION SHOCK ABSORBER |
US4840359A (en) * | 1987-07-23 | 1989-06-20 | Firma Carl Freudenberg | Encapsulated rubber cushion |
GB2211271A (en) * | 1987-10-22 | 1989-06-28 | Freudenberg Carl | Rubber sleeve spring |
EP0324457A2 (en) * | 1988-01-12 | 1989-07-19 | Nissan Motor Co., Ltd. | Vibration isolator of bushing type with liquid chambers in elastic body |
US4865299A (en) * | 1988-03-08 | 1989-09-12 | Tokai Rubber Industries, Ltd. | Fluid-filled cylindrical elastic mount having movable member in fluid chamber |
EP0331916A2 (en) * | 1988-03-08 | 1989-09-13 | Pirelli Sistemi Antivibranti S.P.A. | Elastic bushing |
US4884789A (en) * | 1987-12-28 | 1989-12-05 | Nissan Motor Co. Ltd. | Power unit mounting device |
US4895353A (en) * | 1988-06-28 | 1990-01-23 | The Pullman Company | Fluid filled elastomeric damping device |
US4896868A (en) * | 1988-01-28 | 1990-01-30 | Jean Thelamon | Hydraulic antivibratory support sleeve |
US4899997A (en) * | 1988-09-30 | 1990-02-13 | Lord Corporation | Fluid filled resilient bushing |
US4909489A (en) * | 1988-03-31 | 1990-03-20 | Nissan Motor Co., Ltd. | Mounting device suitable for supporting automotive power units |
US4941649A (en) * | 1988-07-22 | 1990-07-17 | Tokai Rubber Industries, Ltd. | Fluid-filled cylindrical elastic mount having means for improved durability of elastic body |
US4982938A (en) * | 1988-03-26 | 1991-01-08 | Boge Ag | Hydraulic damping elastic bearing |
EP0412662A1 (en) * | 1989-07-14 | 1991-02-13 | Nissan Motor Co., Ltd. | Vibration-damping mounting |
US5035407A (en) * | 1988-06-20 | 1991-07-30 | Nissan Motor Co., Ltd. | Fluid-filled power unit mount |
US5037073A (en) * | 1988-11-10 | 1991-08-06 | Tokai Rubber Industries Ltd. | Fluid-filled cylindrical elastic mount having moveable block and spiral orifice |
US5040774A (en) * | 1990-04-09 | 1991-08-20 | The Pullman Company | Hydraulic damping bushing |
US5044813A (en) * | 1988-01-26 | 1991-09-03 | The Goodyear Tire & Rubber Company | Bush type hydraulically damped engine or transmission mount |
US5048803A (en) * | 1988-12-07 | 1991-09-17 | Boge Ag | Hydraulically damping bearing |
US5054752A (en) * | 1986-12-23 | 1991-10-08 | Nissan Motor Co., Ltd. | Fluid-filled power unit mount |
FR2664954A1 (en) * | 1990-07-19 | 1992-01-24 | Tokai Rubber Ind Ltd | Cylindrical elastic support with fluid filling having lateral and radial elastic walls for desired axial and diametral elasticity characteristics |
US5088702A (en) * | 1989-07-31 | 1992-02-18 | Hutchinson | Hydraulic antivibratory sleeves |
US5088703A (en) * | 1989-12-26 | 1992-02-18 | Bridgestone Corporation | Vibration isolating apparatus |
US5117695A (en) * | 1990-10-12 | 1992-06-02 | Teledyne Industries, Inc. | Vibration attenuation assembly |
US5156379A (en) * | 1987-06-23 | 1992-10-20 | Nissan Motor Co., Ltd. | Fluid-filled insulating bushing |
US5170999A (en) * | 1988-11-25 | 1992-12-15 | Bridgestone Corporation | Vibration isolating device, and method for manufacturing same |
US5221077A (en) * | 1989-05-15 | 1993-06-22 | Bridgestone Corporation | Vibration isolating apparatus |
US5237871A (en) * | 1990-10-12 | 1993-08-24 | Teledyne Industries Incorporated | Vibration attenuation assembly with venting passageway |
US5280885A (en) * | 1988-04-07 | 1994-01-25 | Bridgestone Corporation | Vibration isolating apparatus |
DE4228842C1 (en) * | 1992-08-29 | 1994-05-05 | Freudenberg Carl Fa | Hydraulically damping rubber bearing |
US6349926B1 (en) * | 1998-12-16 | 2002-02-26 | Kinugawa Rubber Ind. Co., Ltd. | Liquid-sealed vibration insulator and method for producing same |
US6511058B1 (en) * | 1999-10-06 | 2003-01-28 | ZF Lemförder Metallwaren AG | Hydraulically damping rubber bearing with uncoupling element |
US6557836B2 (en) | 2001-05-24 | 2003-05-06 | Toyo Tire & Rubber Co., Ltd. | Liquid-filled type vibration isolating device and manufacturing method thereof |
US6585223B1 (en) | 1999-09-14 | 2003-07-01 | Meritor Heavy Vehicle Suspensions, Inc. | Variable compliance bushing |
US6669181B2 (en) * | 2001-04-17 | 2003-12-30 | Bridgestone Corporation | Vibration isolating apparatus |
US6698731B2 (en) | 2002-04-24 | 2004-03-02 | The Pullman Company | High compliance multiple chamber piston for fluid damped elastomer devices |
EP1677027A1 (en) * | 2004-12-31 | 2006-07-05 | The Goodyear Tire & Rubber Company | Elastomeric/hydraulic vibration isolator with adjustable damping |
WO2008119652A1 (en) * | 2007-03-29 | 2008-10-09 | Trelleborg Automotive Technical Centre Gmbh | Elastic bearing bush |
US20110302739A1 (en) * | 2007-10-19 | 2011-12-15 | Whear Frank R | Cross-reference to related applications |
US20120074628A1 (en) * | 2010-09-28 | 2012-03-29 | Hyundai Motor Company | Three point supporting bush type hydromount |
US20120098176A1 (en) * | 2010-10-26 | 2012-04-26 | Tokai Rubber Industries, Ltd. | Fluid-filled cylindrical vibration-damping device |
US8807543B2 (en) | 2009-03-23 | 2014-08-19 | Audi Ag | Elastomeric plain bearing having switchable rigidity |
US20220010858A1 (en) * | 2020-07-08 | 2022-01-13 | Hyundai Motor Company | Hydraulic mount |
US20220196102A1 (en) * | 2019-08-30 | 2022-06-23 | Zhuzhou Times Ruiwei Anti-Viberation Equipment Limited | Formation method for liquid rubber composite nodes with tubular flow channel |
US20220333667A1 (en) * | 2021-04-15 | 2022-10-20 | GM Global Technology Operations LLC | Mount bushing with integrated isolated insert for enhanced high frequency isolation performance |
US11692603B2 (en) | 2021-07-26 | 2023-07-04 | GM Global Technology Operations LLC | Mount bushing with integrated isolated outer insert for enhanced high frequency isolation performance |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4811919A (en) * | 1987-08-06 | 1989-03-14 | Lord Corporation | Volume compensated fluid mount |
JPH01112764A (en) * | 1987-10-27 | 1989-05-01 | Nec Corp | Semiconductor device |
JPH0745891B2 (en) * | 1987-11-06 | 1995-05-17 | 東海ゴム工業株式会社 | Fluid-filled cylindrical mount device |
JP2566476B2 (en) * | 1990-03-06 | 1996-12-25 | 豊田合成株式会社 | Liquid filled vibration isolation device |
JP3050243B2 (en) * | 1990-05-21 | 2000-06-12 | 株式会社ブリヂストン | Anti-vibration device |
JPH04302732A (en) * | 1991-03-29 | 1992-10-26 | Kinugawa Rubber Ind Co Ltd | Liquid sealing type vibration isolation device |
WO2003104675A2 (en) * | 2002-06-07 | 2003-12-18 | Boart Longyear Limited | Vibration isolator |
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JPS60179542A (en) * | 1984-02-24 | 1985-09-13 | Tokai Rubber Ind Ltd | Liquid containing bushing |
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US4588174A (en) * | 1983-03-09 | 1986-05-13 | Tokai Rubber Ind Ltd | Fluid-filled resilient bushing |
US4605207A (en) * | 1983-08-27 | 1986-08-12 | Tokai Rubber Industries, Ltd. | Fluid-filled resilient bushing |
DE3617787A1 (en) * | 1985-05-27 | 1986-11-27 | Bridgestone Corp., Tokio/Tokyo | VIBRATION DAMPER |
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1987
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Cited By (60)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5054752A (en) * | 1986-12-23 | 1991-10-08 | Nissan Motor Co., Ltd. | Fluid-filled power unit mount |
US4817926A (en) * | 1987-04-04 | 1989-04-04 | Firma Carl Freudenberg | Hydraulically damped tubular rubber spring |
US5156379A (en) * | 1987-06-23 | 1992-10-20 | Nissan Motor Co., Ltd. | Fluid-filled insulating bushing |
US4840359A (en) * | 1987-07-23 | 1989-06-20 | Firma Carl Freudenberg | Encapsulated rubber cushion |
GB2211271A (en) * | 1987-10-22 | 1989-06-28 | Freudenberg Carl | Rubber sleeve spring |
GB2211271B (en) * | 1987-10-22 | 1991-10-02 | Freudenberg Carl | Rubber sleeve spring |
US5118068A (en) * | 1987-10-28 | 1992-06-02 | Bridgestone Corporation | Vibration isolator |
FR2622661A1 (en) * | 1987-10-28 | 1989-05-05 | Bridgestone Corp | VIBRATION SHOCK ABSORBER |
US4884789A (en) * | 1987-12-28 | 1989-12-05 | Nissan Motor Co. Ltd. | Power unit mounting device |
EP0324457A2 (en) * | 1988-01-12 | 1989-07-19 | Nissan Motor Co., Ltd. | Vibration isolator of bushing type with liquid chambers in elastic body |
EP0324457A3 (en) * | 1988-01-12 | 1990-03-21 | Nissan Motor Co., Ltd. | Vibration isolator of bushing type with liquid chambers in elastic body |
US4919400A (en) * | 1988-01-12 | 1990-04-24 | Nissan Motor Co., Ltd. | Vibration isolator of bushing type with liquid chambers an elastic body |
US5044813A (en) * | 1988-01-26 | 1991-09-03 | The Goodyear Tire & Rubber Company | Bush type hydraulically damped engine or transmission mount |
US4896868A (en) * | 1988-01-28 | 1990-01-30 | Jean Thelamon | Hydraulic antivibratory support sleeve |
EP0331916A2 (en) * | 1988-03-08 | 1989-09-13 | Pirelli Sistemi Antivibranti S.P.A. | Elastic bushing |
EP0331916A3 (en) * | 1988-03-08 | 1990-12-05 | Pirelli Sistemi Antivibranti S.P.A. | Elastic bushing |
US4865299A (en) * | 1988-03-08 | 1989-09-12 | Tokai Rubber Industries, Ltd. | Fluid-filled cylindrical elastic mount having movable member in fluid chamber |
US4982938A (en) * | 1988-03-26 | 1991-01-08 | Boge Ag | Hydraulic damping elastic bearing |
US4909489A (en) * | 1988-03-31 | 1990-03-20 | Nissan Motor Co., Ltd. | Mounting device suitable for supporting automotive power units |
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Also Published As
Publication number | Publication date |
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JPH0689806B2 (en) | 1994-11-14 |
JPS62167949A (en) | 1987-07-24 |
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